Oscillator means for sonic pile drivers



Dec. 13, 1966 A. G. BODINE, JR 3,291,227

OSCILLATOR MEANS FOR SONIC PILE DRIVERS I INVENTOR. ALBERT 6.' .BoD/N5, di?.

Dec. 13, 1966 A. G. BOBINE, JR 3,291,227

OSCILLATOR MEANS FOR SONIC PILE DRIVERS Filed Jan. 28, 1965 16 Sheetsheet 2 Dec. 13, 1966 A. G. BoD1NE,JR 3,291,227

OSGILLATOR MEANS FOR SONIC PILE DRIVERS Filed Jan. 28, 1965 16 Sheets-Sheet 5 INVENTR.

r TORNEY LBERT 6T 50am/5, di?.

Dec. 13, 1966 A. G. BOBINE, JR 329L227 oscILLAToR MEANS FOR soNIcflLE DRIVERS Filed Jan. 28, 1965 16 Sheets^$heet 4 INVENTOR. y BEHT @Y @f2/N5, r/A.

Dec. 13, 1966 A. G. BODINE, JR i 3,291,227

oscrLLAToR MEANS FOR somo PILE DRIVERS Filed Jan. 28, 1965 16 Sheets-5heet EL?? @K Dec. 13, 1966 A. G. BOBINE, JR

oscILLAToR MEANS FOR somo PILE DRIVERS 16 Sheets$heet 6 Filed Jan. 28, 1965 NE, J?.

TTR/VEY A. G. BOBINE, JR 3,2%,227

OSCILLATOR MEANS FOR SONIC PILE DRIVERS L6 Sheets-Sheet '7 Dec. 13, 1966 Filed Jan. 28, 1965 I. TTRNEY Dec. 13, 1966 A. G. BOBINE, .1R

OSCILLATOR MEANS FOR SONIC PILE DRIVERS 16 Sheetsf-Sheet 8 Filed Jan. 28, 1965 m. m m m Dec. 13, 1966 A. G. BOBINE, .JR 3,291,227

OSCILLATOR MEANS FOR SONIC PILE DRIVERS Filed Jan. 28, 1965 16 Sheets-Sheet 9 f/ I f A 166 I 1V VEN TOR.

TORNEY Dec. 13, 1966 A. G. BOBINE, JR 3,299227 OSCILLATOR MEANS FOR SONIC PILE DRIVERS Filed Jan. 28, 1965 f 16 Sheets-Sheet 10 Z-vgJE.

257 INVENTOR.

: A LBERT'HQD/A/zz BY 2 263 264 y 255 rraR/vey Dec. 13, 1966 Filed Jan. 28, 1965 A. G. BODINE, JR

OSCILLATOR MEANS FOR SONIC PILE DRIVERSv 16 Shee'ts$heet 11 1N VEN TOR. ALBERT @Dm/de rmR/VEY Dec. 13, 1966 A. G. BOBINE, JR 3,291,227

OSGILLATOR MEANS FOR SONIC PILE DRIVERS Filed Jan. 28, 1965 16 Sheets-Sheet l2 28o Fc s 274 bk YQ JNVENTOR. 9 L fnr 6 50p/N5, JA'.

BY Il' r' f7 1 l.. Fc A l rrafP/VEY Dec. 13, 1966 A. G. BOBINE, JR 3,2%,227

OSCILLATOR MEANS FOR SONIC PILE DRIVERS Filed Jan. 28, 1965 16 Sheets-5heet l5 INVENTOR.

Dec. 13, 1966 A. G. BoDlNE, JR' 3,291,227

ATOR MEANS FOR SONIC PILF DRIVERS Fil OSCILL 4 ed 8, 1965 16 heets-$hee |31 442@ /Zgm United States Patent C 3,291,227 OSCILILATGR MEANS FR SONIC FILE DRIVERS Albert G. Bodine, Ir., Los Angeles, Calif. (7877 Woodiey Ave., Van Nuys, Calh't'.) Filed Ian. 28, 1965, Ser. No. 423,728 Claims. {(l. 175-55) This application is a continuation-in-part of my copending application Ser. No. 165,126, filed Ian. 9, 1962, entitled Sonic Pile Driver, now Patent No. 3,189,106.

This invention relates generally to sonic pile drivers, of the class disclosed in prior United States Patent No. 2,975,846, and which may `be characterized generally as comprising means for setting up sonic waves in the pile while exerting a downward biasing Vforce on the pile.

The acoustic theory underlying sonic pile drivers is set forth in said Patent No. 2,975,846, and need not be repeated he-rein in full detail. Brieily, a generator of sonic vibrations, i.e., a vibration generating oscillator, is acoustically coupled to the pile, with proper attention to adjustment of the output impedance of the oscillator to that of the pile with the pile in tight engagement with the earth, so as to set up longitudinal sonic wave action in the pile. The oscillator is operated, broadly speaking, so as to set up a resonant longitudinal standing wave in the pile. Assuming oper-ation in the fundamental frequency `range, the frequency for resonance may range, during operation, between C/ZL and C/4L, where L is the equivalent length of the pile and acoustically coupled-in mass of the pile driver, and C is the velocity of sound in the medium of the pile. For the longer length piles, operation may be at -a harmonic of the fundamental frequency.

Sonic pile driving equipment of this class, embodying a number of features of the present invention, has demonstrated, in eld tests, the ability to out-drive conventional steam hammer pile drivers by `an average ratio of the order of 2O to 1, and in some instances has substantially exceeded that ratio.

Tests carried on to date with equipment of this type have demonstrated the need for powerful sonic drive, flexibility in the drive, accommodation to turning and/ or tilting movements of the pile, and good compliant support for the motor means on the pile, whereby the `motor means rests on the pile, 'but is virtually isolated from the sonic wave action or vibration set up in certain parts of the equipment and in the pile.

Objects of the invention include the provision of a sonic pile driver which is improved 4as regards power, flexibility and `accommodation to movement ot the pile during sonic wave driving, such as twisting or tilting.

A further object is to provide an improved sonic pile driver incorporating a complaint support for the motor means, whereby the motor means exerts weight on the pile, but is compliantly isolated from the sonic frequency vibration of the pile.

A further object is the provision of a flexible driver of novel nature between the motor ymeans and the vibration generator or oscillator driven thereby, such that the oscillator is permitted a large amplitude of vibration, but only `a small proportion of this vibration reaches back to the motor means.

A further object is an orbiting mass oscillator driven by a llexible driver and employing a massive roller with symmetrical internal drive force means.

A further object is such .an intern-a1 drive means having a servo element in said massive roller.

A further object is the provision of a sonic pile driver having a novel means for picking up a pile from a horizontal position iand hoisting it to a vertic-al driving position.

ICC

A further object is the provision of a novel and effective means for increasing the downward biasing force on the pile during driving.

`Other objects will appear in the course of the ensuing description of a present illustrative embodiment of the invention, reference Abeing had to the accompanying drawings, in which:

FIG. 1 is a somewhat diagrammatic perspective view of a sonic pile driving system in accordance with the invention;

FIG. 1a is an enlarged fragmentary view, in side elevation, of the upper end portion of the system of FIG. 1;

FIG. 2 is a front elevational view of the sonic pile driving machine of the invention, shown together with a portion of the leads on which the machine is vertically guided;

FIG. 3 is `a plan view of the machine of FIG. 2, the oscillator and .pile clamping means being shown in phantom lines in a tilted position to facilitate acceptance of the pile from an initial horizontal position at ground level;

FIG. 4 is a side elevational view of the machine of FIG. 3 showing the pile driving machine near the lower end of the leads, and showing, in phantom lines, the oscillator, pile clamp and other portions of the machine tilted into a horizontal position to facilitate acceptance of tle pile from an initial horizontal position at ground leve FIG. 5 is a section taken on line 5 5 of FIG. 3;

FIG. 5a is a detail section taken on line Saz-5a of FIG. 5

FIG. 6 is a section taken on line 6-6 of FIG. 3;

FIG. 7 is an enlargement of a portion of FIG. 6, with parts broken away to show underlying portions in section;

FIG. 8 is a section taken on line 8 8 of FIG. 6, but with the oscillator and other interior parts in elevation;

FIG. 9 is a vertical plan view of the parts inside the exterior casing of FIG. 8;

FIG. 10 is a section taken on broken line 10-10 of FIG. 6;

FIG. 1l is an elevational view of the lower end portion of a tiltable housing of the apparatus, with parts broken away;

FIG. 12 is a section taken as indicated by line 12-12 of FIG. l1;

FIG. 13 is a section taken on broken line 13-13 of FIG. 14;

FIG. 14 is a section taken in accordance with broken line 14-14 of FIG. 13;

FIG. 15 is a section taken on line 15-15 of FIG. 14; FIG. 16 is a detail section taken on line 116-16 of FIG. l2;

FIG. 17 is a detail section taken on line 17-17 of FIG. 14;

FIG. 18 is a section taken on line 18-18 of FIG. 19;

FIG. 19 is a section taken on line 19-19 of FIG. 18;

FIG. 20 is a sectional view taken in accordance with line Ztl- 20 of FIG. 19, but with the crankshaft, servo roller and inertia ring angularly displaced rom the position of FIG. 19, i.e., with the crankshaft turning through its lowermost position;

FIG. 21 is a section taken on line 21-21 of FIG. 20;

FIG. 22 is a section on line 22-22 of FIG. 20;

FIG. 23 is a section on line 23-23 of FIG. 20;

FIGS. 24 and 25 are diagrammatic views illustrating the performance of the vibration generator of FIGS. 20-23;

FIG. 26 is a longitudinal medial sectional View of the pile clamp, being a section on line 26-26 of FIG. 27;

FIG. 27 is a transverse section on line 27-27 of FIG. 26; and

FIGS. 28-31 are sectional views illustrating alternative forms of the vibration generator elements shown in FIGS. 20 and 21.

The invention makes use of certain pile driver transport and handling equipment now conventional in hammertype pile drivers. Thus, as shown in FIG. 1, a vehicle 30 equipped with crawlers 31 pivotally supports, at 32, a boom 33, the upper end of which in turn pivotally supports, at 34, the usual leads 35 comprising a boxframe beam structure including a pair of tublar vertical front legs 36 on and between which a framework for the sonic driving machine 37 is vertically guided, much as in the conventional hammer. The sonic driving machine 37 delivers to the pile P a cyclic force wave characterized by a succession of high amplitude force impulses at a resonant standing wave frequency of the pile, as will be described in more particular hereinafter. A so-called spotter, comprising a telescopic beam structure 38, ladjustable in length, is connected between the Vehicle 30 and the lower end of the leads 35, and conventional cable gear 39 is used to raise and lower the boom, all as is fully understood in the pile driving art, and will require no further description herein. The so-called leads 35 comprise, in addition to the aforementioned vertical front legs 36, a pair of rear legs 36a, and suitable horizontal bracing 36b and diagonal bracing 36C as indicated. The sonic machine is suspended from the upper end of the leads by a block and tackle system as well be described.

While the present pile driver is capable of or adaptable to the driving of various types of pile, such as tubular, open or closed bottom, tubular corrugated, inside or outside mandrel driven, H-section, etc., the invention is here illustrated as driving a tublar pile P (see FIG. 2). The upper end of this pile is rigidly clamped by a hydraulically actuated clamp or coupling means generally designated by the numeral 40, and described in detail hereinafter. As shown best in FIG. 6, a column generally designated by numeral 41, and made up of later described components, extends upwardly from clamp means 40 and carries at its top the vibration generator or oscillator 42. In operation, the body of this oscillator delivers to the upper end of column 41 a cyclic vertically oriented alternating force of large magnitude or impulse, and this cyclic force is transmitted through column 41 and clamp means 40 to the upper end of the pile. The frequency of this cyclic force is made to be in the range of a resonant standing wave frequency of the pile, in general as disclosed in the aforesaid Patent No. 2,975,846.

This sonic pile driving machine of the invention, in its present illustrative form, has `two `separate motor means for driving the oscillator 42, comprising, perferably, and in this instance, two internal combustion engines 44 (FIGS. 2, 3 and 4), disposed on opposite sides of the leads, in end-to-end opposition, with their drive shafts 45 in axial alignment. The common axis of the drive shafts intersects the vertical axis of the pile P and the column 41.

Extending horizontally over and longitudinally of the two engines is a horizontal support lbeam structure 46 (FIGS. 2 and 3) comprised of a center beam 47, two short frame beams 48 bolted to and extending outwardly from the ends of center beam 47, and two tubular engine support beams 49 extending outward from frame beams 48 and overlying the two engines. The two tubular beams 49 have braced flanges 50 suitably secured to mating flanges 51 on the frame beams 48. Tubular beams 49 are closed at the ends and serve as air receivers, for a purpose to be mentioned hereinafter. A standard compressor, not shown, maintains these receivers lled with air under necessary compression. Extending laterally and downwardy from the tubular beams 48 are engine support framing means including lateral members 53 and vertical channel members 54 carrying engine support brackets 55 (FIGS. 3, 4 and 5). Connected to the lower ends of members 54 are lower horizontal frame members 56. Platforms 58 extend rearwardly from the rearward frame members 56 (FIGS. 3 and 4) and on at least one of these platforms is erected a hand rail 59 and a seat 60 for an operator. An instrument panel, in convenient reach of the operators position, is indicated at 61.

Fuel tanks for the engines are indicated at 62, supported below the engines by frame members 56, and the engines are shown with exhaust pipes 63, muiers 64, and air cleaners 65 (FIG. 2).

The entire sonic machine may be hoisted or lowered by means of block and tackle gear 66 including double sheaves 67 in the top of the leads, a cable 68, and a block 69 having an eye 70 for connection of one end of the cable `68, and a sheave 71, mounted at the center of beam 46 (FIGS. 1-5). The cable 63 goes from eye 70 over one sheave 67 at the top of the leads, then down and around sheave 71, then up and over the second sheave 67, then down the back of the leads over guide sheaves 72a and 72b, under a sheave 73 mounted on the leads adjacent the upper end of boom 33, under another sheave 74 near the lower end of the boom, and thence to a power winch (not shown) within the vehicle 30. During hoisting or lowering movement of the sonic machine by this cable system, the machine is guided by the tubular members of the leads 36, as later described.

The frame beams 48 have depending double-walled legs 75 (FIGS. 5, 6 and 7) formed, in axial alignment with the engine drive shafts, with inwardly projecting hubs 76. These hubs 76 receive bearing sleeves 77 containing roller bearings 78 for drive sleeves 79 formed with internal splines 80.

As shown best in FIG. 7, each of the aforementioned engine shafts 45 is coupled through coupling 83 to a cup 84 containing internal splines 85, and a drive shaft 86 has on one end a head 87 received inside cup 84 and formed with arcuate splines 88 meshing with spline 85, and has on the other end a head 90 received inside the corresponding end portion of sleeve 79 and formed with arcuate splines 91 meshing with splines 80. The arcuate splines on heads 87 and 90 permit the shaft 86 to move angularly through a limited extent while driving the sleeve 79 from the engine shaft 46. Received in the opposite end portion of sleeve 79 is a head 94, provided with arcuate splines 95 meshing with sp-lines 80, and formed on the end of a shaft 96. The other end of this shaft 96 drives certain gears leading to the oscillator, as will later be explained. An intermediate partition 97 in sleeve 79, engageable by heads 91 and 95, limits endwise r7no-vement of the shafts 86 and 96 inwardly into sleeve The two frame hubs 76 (FIG. 6) form axially aligned trunnions, on which the oscillator and certain associated gearing and other components of the mechanism are pivotally mounted. Bearing bushings 100 (FIG. 7) surround trunnions 76, and rotatable on bushings 100 are frame members or collars 101 which are disposed about the trunnions, and to which are welded a top frame ring 102. An inner cylindrical wall 103 is welded to the inner edge of ring 102 and to members 101, and an outer cylindrical wall 104 is welded to the outer edge of ring 102, just outside members 101, and being apertured, as at 105 (FIG. 7), to receive outwardly projecting annular portions 106 of the members 101.

A heavy frusto-conical plate 108 is welded to walls 103 and 104, just below collars 101, and carries, at its lower, inner edge, a mounting ring 109 engaged by a peripheral ange 110 on the rim of a heavy support plate 111, to be described in more detail hereinafter, but which may be stated at this point to be supported compliantly, in the vertical direction, by the upper end of an air spring generally designated at 112. It may also be stated at this point that the weight of the two engines is imposed through the beam 46, frame legs 75, trunnions 76, frame collars 101, cylindrical walls 103 and 104, frusto-conical plate 108, and plate 111, onto the upper end of the air spring. In fact, as will appear from what follows, the

weight of the entire machine, excepting for the oscillator 42, its supporting column 41, the later described air spring pistons, and the hydraulic pile clamp dil, is transferred through the plate 111 to the upper end of the air spring. The air under compression in this air spring 112 transfers this entire load compliantly to the aforementioned column d1 mounted on the pile, and thus to the pile, as presently to be described. lt will further Ibe seen that the beam structure d6, engine support means carried directly thereby, and the -beam arms 75, comprise a main framework adapted for vertical guidance by the leads; while trunnioned to the arms 75 of this framework is a frame means 1111, 102, 1113, 11i-i, 168 and 111 imposing the load of this structure on the top of the air spring.

The air spring 112, in a present illustrative form, is made up as follows (FlGS. 6, 13, 14 and l5): The hydraulic clamp 4@ for the pile includes an upper inverted cup 115 (FIGS. 6 and 26) having a marginal ilange 116 secured, as by screws 117, to the bottom of a lower inverted clamp cup 118, into which the upper end of the pile is received and clamped, as later described. The upper cup 115 has a cylindrical side wall 119, and a flat top 121i provided with a central boss 121. Mounted on the top 120 of cup 115 is the lowermost of a plurality of circular plates 124, here three in number, serving as pistons of the air spring. The two plates 124 above the lowermost one are separated from the latter and from each other by thick spacer washers 125, and a cylindrical head 126, of the same diameter as the washers, seats on the uppermost plate 124. The plates 124 have central positioning apertures 124g receiving the boss 121 on cup 115, and receiving similar bosses 127 formed on the washers 125 and head 126. The cup 115, spacer washers 125 and head 126 are connected by tie rods 136, the upper ends of which are threaded into a flange 131 o-n the lower end of a tubular stem 132 forming -an upper portion of the column 41, and the lower end of which are threaded to receive nuts 133, as shown. An enlarged cylindrical head 13d at the upper end of stem 132 is secured, as by studs 135, to the cylindrical base part 136 of the oscillator body 137. The cup 115, plates 124i, washers 125, heads 125, and stem 132, comprise the aforementioned column 41 by which the oscillator body is supported on the upper end of the pile.

The piston plates 124 are positioned in chambers 14511 whose side walls are defined by cylindric rings 141. Engaging and sealed to the uppermost ring 141 is an air spring cover plate 143, bearing the down load of the plate 111, and formed with a central bore 14d (FlG. 13) which receives, with a small clearance, the head member 126 of column llt-1. vertically spaced piston rings 115 are used around the head member 126 to allord a pressuretight seal, as shown.

At the bottom of the air spring assembly is a bottom cover plate 147 (FIG. 13), engaging the lower end of the lowermost ring 1421, and bore, as at 1117er, to receive, with clearance, the cylindrical side wall 117 of cup 115. The plate 147 is counteirbored to receive a bronze bearing bushing 1418 for the clamp cup wall 119, and piston rings 1419 seal the cover plate 1417 to said wall 119.

Between the rings 141 are spacer rings 1511 formed with partition walls 151 which carry bushings 152 (FIG. 13) fitting spacer washers 125 with small annular clearance, pressure-tight seals being provided therebetween by means of piston rings 153. The assembly of rings 1411 and and upper and lower cover plates 143 and 147, is secured by long bolts 141:1, making up air spring housing 15d. The peripheries of the piston plates 124 carry piston rings 155 which afford pressure seals with the cylindric inside surfaces of the ring 141.

Air under pressure is supplied to air spring chambers 14u as shown best in FIG. 13. The pressurized air is coneyed via a hose 156 to a litting 156g: on the rim of cover plate 14,3. Hose 156 leads from a tting 156b on the inside of a later described housing wall, which is fed through connector 156C (FIGS. 11 and 12) on the outside of said 'wall from a hose, not illustrated, but which will be understood to lead from any suitable source of air under pressure, for example, one of the pressure reservoirs 49. The air entering fitting 156a passes through a pair of metering orilices 157 to passages 158 extending vertically through rings 141 and 151). Upper and lower ports 159 and 161) in rings 141 provide communication between passages 15S and the chamber spaces above and below the pistons 12d, so that air under pressure is delivered to both of said chamber spaces. The piston rings in the edges of pistons 124 control orilices 162 (FlG. l5) in the rings 1411 leading to vertical air discharge passages 163. As seen in FIG. 14, there are a number of the vertical discharge passages 163, and a corresponding plurality of the orices 162. In the midpositions of the pistons, the orifices 162 are closed by the piston rings 155. Whenever the downward loading imposed on the air spring housing 154 exceeds a predetermined value, the air spring housing lowers relative to the pistons 124, so that orifices 162 communicate wholly or partially with the chamber spaces below the pistons. A quantity of pressure air is thus discharged from below the pistons, so that there is a pressure differential across each piston in the downward direction. lt will be seen that this pressure differential is such that an upward force is exerted on the air spring housing, so that the latter then tends to rise. The system seeks and tends towards a condition characterized by bodies of air under compression above and below the several pistons, and with sulicient -continuous or periodic discharge of air below the pistons to afford regulated air pressures and a regulated pressure differential which furnishes air spring support for the air spring housing and parts resting thereon. During pile driving, the pistons 1211 oscillate vertically, while the air cushions between the plates and the air spring housing virtually isolate the latter from such oscillation. At the same time, the parts resting on the air spring housing are vertically supported by the air under compression in the air spring, and whatever minor vertical vibration, if any, that may occur in the air spring housing is accommodated by the compressed air in the air spring.

lt will be seen that the air spring cover has on its underside an annular abutment lfor the Iuppermost piston plate 12d, normally spaced thereabove, but furnishing a stop shoulder engageable against the uppermost plate 124 in event of loss of pressure in the chambers 141i above the plates 12d. Similarly, the lower air spring cover 147 has an annular abutment 166, which is eng-ageable against the lowermost plate 124i in event of an upward pull being taken on the air spring housing (under conditions to be described later) in event of' loss of pressure in the chambers 141i below the plates 124i. ln normal operation, the piston plates` 12d have a vibratory travel range which terminates short of the abutment shoulders 165 and 166.

Referring again to the supporting plate 111, and to FlG. 6, the periphery of said plate, as explained above, has a peripheral flange or mounting rim portion 110. inside said rim portion, the plate has a channel portion 1711 (the reason for the shape of which will appear hereinafter) inside of which is a centrally apertured dished or arcuate portion i171, defined by arcs struck about a center point T (FIG. 6) which is at the intersection of the axes of the engine shafts with the vertical axis of the column 41 and the pile. This arcuate portion 171 surrounds the hub portion 173 on the top of cover plate 143, there being a substantial annular clearance between these parts, as shown. A bearing ring 174 seated in a pocket in the top of plate 143 has a concave arcuate upper face mating the convex arcuate lower face of plate portion 171. A bearing ring 176 has a convex arcuate lower face mating the concave upper face of plate portion 171. This bearing ring 176 lits onto the tubular lower end portion 173 of a sleeve 181i, said tubular portion 178 engaging an annular seat on air spring cover 143 and being secured thereto, as shown best in FIG. 6. The arcuate portion 171 of plate 111 has a free-sliding t between the bearing rings 174 and 176.

Sleeve 180, has, just above tubular portion 178, an annular flange 181, the underside of which engages bearing ring 176, and which in turn supports certain parts of the mechanism, as will presently appear. The sleeve 18() rises to a level just above the lower end of the cylindrical base part 136 of the oscillator body or housing, having at its uppermost end an internal shoulder 183 which fits oscillator base part 136 and cylindrical head 134 of stem 132 with clearance, and under which is confined a bronze bearing bushing 184 for said cylindrical head 134.

Referring again to FIGS. 6 and 7, the aforementioned shafts 96, understood to be driven in opposite directions on their common axis from the two engines, have on their ends nearest the pile axis heads 19t) formed with arcuate splines 191 which mesh with internal splines inside the bores -of bevel gears 192. Each of these gears 192 has a sleeve portion 193 t-urning in a bearing 194, the outer cylindrical case 195 of which has an intermediate mounting flange 196. The two bearing cases 195 are received in cylindrical openings 197 formed in opposite sides of a frame ring 198 supported on and secured to a peripheral portion of the aforementioned flange 181, as clearly shown in FIGS. 6 and 7. The bearing mounting flanges 196 engage the frame ring 198 around the openings 197, and are secured thereto as shown.

Oppositely rotating bevel gears 192 mesh with a ring gear 200 which surrounds sleeve 180, with annular clearance, and which is secured to an annular ange 210 on the lower end of a telescopic drive sleeve assembly 211 (FIG. 7) surrounding and relatively rotatable about the aforementioned sleeve 180. Preferably, the sleeve assembly 211 includes a lower sleeve portion 212 reaching upwardly from ange 210, and carrying a bronze bushing 213 rotatable on sleeve 180, an opposed upper sleeve portion 214 spaced above sleeve portion 212, and carrying a bronze bushing 215 also rotatable on sleeve 180, and an intermediate interconnecting sleeve 216 having portions overlapping said upper and lower sleeve portions 212 and 214, and drivingly connected therewith by splines 218.

The ange 210 at the bottom of the drive sleeve assembly 211 has secured to its bottom a bronze bearing ring 220, which bears against and turns on the flange 181. The upper side of this ange 210 engages a bronze bearing ring 220 supported by frame ring 198 (FIG. 6). The upper end of the upper sleeve portion 214 of Sleeve assembly 211 has integrally formed therewith a ring gear 221, meshing with and driving, in opposite directions on their common axis, two bevel gears 222 of a turret 224 through which the oscillator 42 is driven. The telescopic feature of sleeve assembly 211 is for the accommodation of longitudinal expansion or contraction owing t-o temperature changes, and is such as to assure that the Working parts at both the upper and lower ends of this sleeve assembly maintain proper positions with reference to bearing surfaces, gears, etc.

The aforementioned bevel gears 222 are 4on gear sleeves 230 (FIG. 6) journalled in suitable bearings in bearing housings 231 which are secured in opposite sides of a turret frame ring 232, and the latter has at the bottom a tubular extension 233 and a downwardly presented bearing face 234 outside thereof which engage a bronze bearing ring 235 seated in the previously described frame ring 198. Turret frame ring 232 is thus rotatable on frame ring 198. Turret frame ring 232 also has, at the top, an internal cylindrical bearing surface 238 and an upwardly facing `bearing surface 239 which engage a bronze bearing ring 240 secured to a flange 241 on. the upper end of a cap member 242 secured over and to the upper end f sleeve 180.

Secured to turret frame ring 232, at diametrically opposite locations thereon, are gear housing assemblies 250, accommodating certain oscillator gears and bearings therefor as will now be described. Each of the bevel gears 222 is internally splined, as at 251, to a shaft 252 which drives a spur gear 253 suitably journalled in the associated housing assembly 250. The gear 253 drives a spur gear 254, which in turn drives a gear 255, and the latter is on a shaft 256 carrying a larger gear 257 which meshes with and drives a gear 258 (see FIG. 18)` Gear 258 is on a gear sleeve 260 carrying a flywheel 261, and has internal splines 262 meshing with arcuate splines 263 on a spheric head 264 at one end of a drive shaft 265, the other end of which has a head 266 carrying arcuate splines 267 which mesh with splines 268 inside a coupling 269 to one side of oscillator 42. As will appear from FIGS. 6 and 9, the two gear housing assemblies 250 are so arranged that the tw-o drive shafts 265 are parallel to one another, are on opposite sides of the oscillator 42, and are aligned with opposite halves of the latter. Also, the gear trains are so arranged that the two shafts 265 rotate in opposite directions, as will be evident.

The oscillator contains means driven by the two shafts 265 by which the massive oscillator body 137 is set into relatively low amplitude but high force vertical vibration, and this means may, as in many known applications in the prior art, comprise two unbalanced -or orbital rotors, one rotated by each of the two oppositely rotating shafts, with the rotors journalled in the body 137, and with their unbalanced masses so synchronized as to move vertically in unison, and laterally toward and from one another in unison. In such a device, the two unbalanced rotors, with their centers of gravity describing orbital paths, generate reaction forces on the body 137 which are additive in the vertical direction, but which cancel one another in the lateral direction. Powerful vertically oriented vibration forces are thereby exerted on the device on which the generator body 137 is mounted.

However, I have here shown a preferred, improved oscillator having a number of functi-onal advantages, which are unique and of special efficacy in a powerful sonic machine of the present character, and which has exhibited outstanding performance.

The oscillator body 137 is horizontally elongated, forming a sort of massive T-head 270 on the top of its cylindrical base part 136. This T-head has fiat side faces 271 and 272, and contains parallel transverse bores 273 extending between these faces, one in each half of the T-head, and the two bores being aligned with the two aforementioned oscillator drive shafts 265. These bores 273 are lined with tightly fitted hardened steel bushings 274.

Clamped to the projecting end porti-ons of the bushings 274 are end plates 276, the inside surfaces of which detine, with bushings 274, two cylindrical chambers 278 for two relatively massive hollow cylindrical rollers o1' rings 280 having axial bores 281. With reference to FIGS. 18 and 19, the rings 280 are caused to roll around the inside surfaces of the bushings 273 in opposite directions by means of servo-rollers 282 which are inside of the bores of the rings 280, and which are driven in opposite direction in orbital paths by crank mechanisms 233 from oppositely rotating oscillator drive shafts 265, as shown and diagrammed in FIGS. 20-25 in addition to FIGS. 18 and 19. Note that FIGS. 20-25 show the rings 280 and arms of the crank mechanisms in different positions from those of FIGS. 18 and 19, i.e., at the bottoms of their paths of travel. The rings 280, in rolling around the bushings in the -oscillator body 137, exert centrifugal forces against the latter, and the servo-rollers and their driving crank mechanisms are initially so synchronized that the rolling rings move vertically in unison, and toward and from one another in unison, so that vertical forces exerted thereby `on the oscillator body 137 are 

1. A VIBRATORY PILE DRIVE COMPRISING AN OSCILLATOR FOR GENERATING AN ALTERNATING FORCE IN THE DIRECTION IN WHICH A PILE IS TO BE DRIVEN, SAID OSCILLATOR HAVING A POWER INPUT SHAFT AND A VIBRATING BODY, A COUPLING FOR COUPLING SAID VIBRATING BODY TO THE PILE AND A MOTOR AND TRANSMISSION FOR DRIVING SAID POWER INPUT SHAFT, WHEREIN A VIBRATION ABSORBING SUPPORT IS PROVIDED WHICH IS CONNECTED TO SAID VIBRATING BODY AND WHICH SUPPORTS SAID MOTOR AND TRANSMISSION, SUBSTANTIALLY ISOLATING SAID MOTOR AND TRANSMISSION FROM SAID ALTERNATING FORCE, SAID TRANSMISSION INCLUDING AN OUTPUT COUPLING SHAFT WHICH IS SUBSTANTIALLY PERPENDICULAR TO THE DIRECTION IN WHICH THE PILE IS TO BE DRIVEN, WHICH IS AXIALLY ALIGNED WITH SAID POWER INPUT SHAFT AND WHICH HAS UNIVERSAL JOINT COUPLINGS AT ITS OPPOSITE ENDS, AND WHICH OSCILLATOR HAS A LARGE ROLLER ORBITING AROUND A BEARING RACE IN SAID VIBRATING BODY, AND WHICH POWER INPUT SHAFT IS ARRANGED TO DELIVER DRIVE FORCE WITHIN A COAXIAL BORE IN SAID MASSIVE ROLLER. 